EP2703686B1 - Fourche suspendue, en particulier pour vélos - Google Patents

Fourche suspendue, en particulier pour vélos Download PDF

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Publication number
EP2703686B1
EP2703686B1 EP13004217.9A EP13004217A EP2703686B1 EP 2703686 B1 EP2703686 B1 EP 2703686B1 EP 13004217 A EP13004217 A EP 13004217A EP 2703686 B1 EP2703686 B1 EP 2703686B1
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EP
European Patent Office
Prior art keywords
chamber
throttle valve
damping
valve
damper
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
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Application number
EP13004217.9A
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German (de)
English (en)
Other versions
EP2703686A3 (fr
EP2703686A2 (fr
Inventor
Martin Walthert
Stefan Battlogg
Jürgen PÖSEL
Michael Kieber
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DT Swiss AG
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DT Swiss AG
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Publication of EP2703686A2 publication Critical patent/EP2703686A2/fr
Publication of EP2703686A3 publication Critical patent/EP2703686A3/fr
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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B62—LAND VEHICLES FOR TRAVELLING OTHERWISE THAN ON RAILS
    • B62K—CYCLES; CYCLE FRAMES; CYCLE STEERING DEVICES; RIDER-OPERATED TERMINAL CONTROLS SPECIALLY ADAPTED FOR CYCLES; CYCLE AXLE SUSPENSIONS; CYCLE SIDE-CARS, FORECARS, OR THE LIKE
    • B62K25/00—Axle suspensions
    • B62K25/04—Axle suspensions for mounting axles resiliently on cycle frame or fork
    • B62K25/06—Axle suspensions for mounting axles resiliently on cycle frame or fork with telescopic fork, e.g. including auxiliary rocking arms
    • B62K25/08—Axle suspensions for mounting axles resiliently on cycle frame or fork with telescopic fork, e.g. including auxiliary rocking arms for front wheel
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
    • F16F9/10—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium using liquid only; using a fluid of which the nature is immaterial
    • F16F9/14—Devices with one or more members, e.g. pistons, vanes, moving to and fro in chambers and using throttling effect
    • F16F9/16—Devices with one or more members, e.g. pistons, vanes, moving to and fro in chambers and using throttling effect involving only straight-line movement of the effective parts
    • F16F9/18—Devices with one or more members, e.g. pistons, vanes, moving to and fro in chambers and using throttling effect involving only straight-line movement of the effective parts with a closed cylinder and a piston separating two or more working spaces therein
    • F16F9/185—Bitubular units
    • F16F9/187—Bitubular units with uni-directional flow of damping fluid through the valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
    • F16F9/32—Details
    • F16F9/53—Means for adjusting damping characteristics by varying fluid viscosity, e.g. electromagnetically
    • F16F9/535—Magnetorheological [MR] fluid dampers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
    • F16F9/32—Details
    • F16F9/53—Means for adjusting damping characteristics by varying fluid viscosity, e.g. electromagnetically
    • F16F9/535—Magnetorheological [MR] fluid dampers
    • F16F9/537—Magnetorheological [MR] fluid dampers specially adapted valves therefor

Definitions

  • the present invention relates to a suspension fork for bicycle.
  • a suspension fork comprises a control tube and at least one pipe system connected thereto, which comprises a standpipe and a dip tube which is movable relative thereto and in particular telescopable.
  • a Radfactraum is provided.
  • the suspension fork as is often the case, has two parallel pipe systems, the wheel storage space is located between the pipe systems.
  • the damping fluid used is usually an oil-based damping medium, which passes through one or more damping gaps for damping. Due to the different damping channels and the different damping valves, suspension forks are usually very complex. A particular problem with suspension forks for human-powered vehicles and especially bicycles is the volume of construction. Another important factor is the weight, which is particularly important for sporty bicycles and especially for suspension forks for the competition and for the demanding amateur sector of particular importance. Furthermore, it is advantageous if at least individual parts of the suspension fork have such dimensions that they can be used on other suspension forks. In any case, the installation dimensions must be adhered to. Another important criterion is the possible travel.
  • the damping in the compression stage and the damping in the rebound stage are usually set separately via a multiplicity of mechanically adjustable valves.
  • different flow paths are provided for low-speed damping and high-speed damping.
  • blow-off valves may still be provided which open in the case of particularly strong impacts in order to avoid excessive loads.
  • Forks can be simpler in which, for example, magnetorheological or electrorheological fluids are used as the damping medium, since there the damping fluid flowing through a damping channel can be exposed to a suitably adjustable magnetic or electric field, whereby the desired damping is adjustable and can be controlled differently as needed.
  • the known damper has a circuit of a magnetorheological fluid, wherein the MRF valve is always flowed through by one-way valves always in the same direction.
  • Such a known damper works in principle, but has a relatively high weight.
  • the EP 1 394 439 A1 discloses a bumper system for bicycles with an electrorheological and / or magnetorheological fluid, wherein a controllable valve is flowed through by the electrorheological and / or magnetorheological fluid and is driven accordingly to set a desired damping.
  • electrorheological fluids require high voltages, so that a damper according to this document in the event of a fall offers certain potential dangers.
  • relatively large metallic surfaces are needed to control, which increase the weight.
  • a suspension fork according to the invention is provided for an at least partially muscle-operated vehicle and in particular a bicycle.
  • the suspension fork comprises a control tube and at least one pipe system connected thereto.
  • the pipe system has a standpipe and a relatively movable dip tube.
  • the standpipe and the dip tube are made telescopic.
  • a Radfactraum is provided. If the suspension fork comprises two pipe systems, the wheel storage space is provided between the pipe systems.
  • a damper device is provided with a damping medium.
  • the damper device has a damper chamber and a throttle valve.
  • the damper chamber is divided by a movable piston into a first chamber and a second chamber.
  • the piston is connected to a piston rod.
  • the first chamber is connected via a return flow, the throttle valve and a connecting channel with the second chamber.
  • a magnetorheological fluid is provided as a damping medium.
  • the throttle valve is controllable. It is at least a field generating means for generating an adjustable magnetic field provided in a damping channel of the throttle valve.
  • a control device is used for control.
  • At least substantially a one-way circuit is provided for the damping medium.
  • At least two one-way valves are provided in the one-way circuit. Both during immersion of the piston rod into the damper chamber into as well as when extending or evacuation of the piston rod from the damper chamber out the damping medium flows in the same direction of rotation.
  • a first one-way valve is arranged on the piston, which allows a flow and in particular only a flow of the damping medium from the second chamber into the first chamber.
  • a second one-way valve is arranged on the connecting channel, which allows a flow and in particular only a flow of the damping medium from the connecting channel into the second chamber.
  • both the immersion of the piston rod in the damper chamber into and the extension or dewatering of the piston rod from the damper chamber out with the controllable throttle valve is targeted and, if necessary, also adjustable.
  • An insertion device is provided between the pipe system and the damper chamber, wherein the return flow channel is provided at least in sections on the insert device and preferably limits the flow cross section of the return flow channel.
  • An average density of the insert between the pipe system and the damper chamber is less than an average density of the damping medium.
  • the throttle valve is disposed axially adjacent to the damper chamber.
  • the axial distance is in particular smaller than half the length of the damper chamber.
  • the suspension fork according to the invention has many advantages.
  • a significant advantage of the easily controllable suspension fork according to the invention consists in the simple structure, which is characterized by in the pipe system provided disposable circuit results.
  • the damping medium flows from the second chamber through the one-way valve in the piston in the first chamber during compression, when the piston is further immersed in the damper chamber. Through the return flow channel, the damping medium passes through the throttle valve, if necessary, back into the second chamber.
  • the damping force can be easily adjusted by different strength magnetic fields.
  • An additional blow-off valve is not necessary because the properties of magnetorheological fluids reversibly break up the interlinkage between the individual particles when a limit load is exceeded.
  • the one-way valves arranged on the piston or on the connection channel can not only be provided on the outside of the respective bodies, but also be arranged at a distance therefrom, provided they are directly connected thereto.
  • the term "on” in the context of the present invention also includes the term "in”, so that the one-way valves can also be provided in the piston or in the connecting channel.
  • a compensation chamber is provided with a particular biased compensation volume.
  • the balance volume is connected to the throttle valve and the second chamber.
  • the compensating volume is connected in particular via the connecting channel with the second chamber.
  • the first switching valve it is possible, the compensation chamber and the compensation volume always in the low pressure range, d. H. to switch behind the throttle valve (s).
  • the compensation volume so no extension force on the piston, which significantly improves the response.
  • the piston When immersed, the piston displaces a volume which is proportional to its cross-sectional area. In the first spring chamber, however, only a volume is released, which is proportional to the cross-sectional area of the piston minus the cross-sectional area of the piston rod. Therefore, upon immersion of the piston, a portion of the damping medium must flow through the return passage to the throttle valve. There is a corresponding throttling instead. This part of the damping medium then enters the compensation chamber.
  • the compensation chamber is arranged axially spaced from the piston.
  • the compensation chamber is arranged axially adjacent to the damper chamber and advantageously preferably axially adjacent to the second chamber.
  • the throttle valve is connected via a first check valve to the compensation chamber.
  • the first check valve allows only a flow of the damping medium from the throttle valve into the compensation chamber.
  • the compensation chamber is connected via a second check valve to the second chamber.
  • the second check valve allows only a flow of the damping medium from the compensation chamber into the second chamber.
  • At least one of the check valves is adjustable in order to allow an adjustable flow resistance in the compression stage and / or the rebound stage.
  • the compensation chamber is connected via two separate compensation channels with the connecting channel.
  • One equalization channel is provided with the first check valve, while the second equalization channel is equipped with the second non-return valve.
  • the check valves from outside the fork are adjustable to change the characteristic curve, for example, in mechanical check valves.
  • the check valve is designed as an adjustable throttle valve with non-return device. If a mechanical throttle valve is used in such an embodiment, the basic characteristic curve is set with the throttle valve, for example, while the two adjustable ones can be set Check valves, for example, the basic characteristic curve is adapted to the desired characteristic in Switzerlandprocessnfall and the desired curve in the compression stage case.
  • the damping medium comprises at least one magnetorheological fluid and in particular the damping medium is designed as a magnetorheological fluid (MRF).
  • the throttle valve is preferably designed controllable and comprises at least one field generating device for generating a magnetic field in at least one damping channel of the throttle valve.
  • throttle valve is designed to be controllable and generates a correspondingly controlled magnetic field in the damping channel of the at least one throttle valve.
  • a control device is used for the control.
  • ERF electrorheological fluids
  • MRF magnetic field strength of a permanent magnet
  • the magnetic field strength of a permanent magnet is permanently adjusted by, for example, a short magnetic pulse.
  • the set magnetic field strength is maintained long after the magnetic pulse, without further external energy is needed.
  • Such an embodiment is particularly advantageous because magnetorheological damping media react quickly to applied magnetic fields.
  • a permanent magnet is used as a field-generating device.
  • a permanent magnet can be mechanically changed in its position in order to be able to change the damping force acting in the damping channel.
  • a permanent magnet is used whose magnetic field is superimposed by the magnetic field of an electric coil depending on the requirements just desired.
  • a permanent damping can be adjusted by the permanent magnet, for example, if necessary, by the magnetic field the electric coil is attenuated or amplified.
  • the field generating device comprises a so-called remanence magnet, the magnetic field strength of which is periodically adjusted as needed or at irregular intervals by a magnetic pulse of an associated electrical coil.
  • a remanence magnet is permanently set by the magnetic pulse of, for example, only a few milliseconds duration to a specific magnetic field strength. If the magnetic magnetic field strength of the remanence magnet is to be reduced again, this can, for. B. via a temporally weakening alternating field.
  • a solution for the basic structure of a throttle valve with a remanence magnet can in particular the EP 2 339 203 A2 be removed.
  • a preferred construction of a valve operating with remanence is preferably based on this document.
  • a particularly flexible control of the damping properties is possible.
  • a controllable throttle valve provides the ability to control in real time, responding to a shock in real time, even as the shock increases and before it reaches its maximum. This can be ensured here by the reaction rate of a, for example, magnetorheological fluid, which can concatenate within a millisecond or a little more along the field lines of a magnetic field and thus can greatly increase the flow resistance transversely thereto.
  • At least one control device and at least one sensor device are preferably provided.
  • the control device the controllable throttle valve can be adjusted in dependence on sensor signals.
  • a wide variety of sensors can be provided.
  • at least one sensor device is provided to detect a measure of a relative speed.
  • the sensor device is provided to detect a measure of a relative speed of the piston to the damper chamber.
  • a sensor device detects a relative speed of the standpipe and the dip tube to each other.
  • a relative speed of the standpipe is detected, for example, in the vertical direction in order to conclude from the current load can.
  • At least one sensor device is provided to detect a direction of the relative movement between the piston and the damper chamber.
  • This is z. B. in the use of magnetorheological fluids of importance, since no indication can be made about whether it is flowing damping medium in a compression process or a rebound easily by the flow of the damping medium within the one-way cycle.
  • at least one sensor device for detecting the direction of the relative movement may be provided, which comprises, for example, at least one deflectable spring plate, which is preferably biased by corresponding preloading in a center position.
  • Such a sensor device can be provided, for example, in the compensation chamber or on a compensation channel leading to the compensation chamber.
  • spring plate With the deflection of the example used as a detector spring plate can be detected whether the damping medium flows out of the compensation chamber or into it. Accordingly, it can be determined with the deflection of the detector, whether a compression or rebound operation is present.
  • the detector must be arranged only in an area which is flowed through by the damping medium in both cases. It is also possible that two separate sensor devices are provided which detect separately the compression and the rebound.
  • a sensor device which detects a measure of a travel. Due to the temporal change of the spring travel can be concluded that whether the fork springs or springs. It is also possible to use at least one acceleration sensor, from whose or their data can be concluded on a compression or rebound.
  • At least one cushioning be provided.
  • Such cushioning may increase the damping in an end region during compression or rebounding accordingly, to prevent a breakdown of the fork.
  • the first chamber is disposed below the second chamber in intended use.
  • the throttle valve is disposed above the damper chamber.
  • the compensation chamber is provided above the throttle valve. The compensation chamber may also be provided below or laterally of the throttle valve, which reduces the flow paths.
  • a particularly simple structure is made possible.
  • refilling the compensation chamber with compressed air for example, can be done easily.
  • the above-arranged throttle valve or arranged above the compensation chamber also allows easy refilling or easy replacement of the damping medium. The heat dissipation can be done easily because in the upper region of the fork, the standpipe is no longer or no longer always surrounded by the dip tube.
  • a considerable advantage of such an embodiment is also that the space available in a suspension fork can be advantageously utilized. While usually only a small diameter is available, can be exploited within the standpipes or dip tubes whose length.
  • the inserting device By the inserting device, the flow cross section of the Return flow channels are significantly reduced.
  • the total weight of the fork can be significantly reduced, which is a considerable advantage for high demands.
  • a maximum length, extension or a largest diameter of a flow cross-section of the return flow channel at the insert device is smaller than a diameter of the pipe system.
  • a maximum length or a largest extent of the flow cross section at the insert device is smaller than a radius transversely to the flow direction and particularly preferably smaller than a half radius of the pipe system.
  • the dimensions of the pipe system relate here to the outer diameter and particularly preferably the inner diameter of the standpipe.
  • the gap between the outer wall of the damper chamber and the inner wall of the dip tube is used completely as a flow channel.
  • the entire space between the outer wall of the damper chamber and the inner wall of the standpipe would be filled with the damping medium here. Due to the significant volume of this gap there would be a significant amount of damping medium available, which would increase the total weight of the fork quite considerably.
  • a solution for reducing the weight could be to reduce the gap in which, for example, the interior or the inner diameter of the standpipe is reduced. This would result in a smaller gap, so there would be a lower mass of damping medium available. But such a solution would have the disadvantage that the compatibility of the fork with the dimensions commonly used would no longer exist. It could not standpipes and dip tubes are used, as they are currently common. That would make the construction of such a fork considerably more expensive.
  • the outer diameter of the damper chamber could be increased to allow a smaller gap in the gap. Even with this solution would be a lesser Collect mass of damping medium in the gap so that the weight would be reducible.
  • a disadvantage of this solution is that the wall friction in the flow of the damping medium would increase considerably. This would make it difficult to adjust the required damping properties, since low damping values would practically no longer be adjustable due to the high flow resistance in the intermediate space. Incidentally, even with a reduction in the inner diameter of the standpipe, a corresponding increase in the flow resistance of the damping medium would result. This means that both a reduction of the diameter of the standpipe and an enlargement of the damper chamber does not offer a satisfactory solution.
  • the amazing solution now is to position at least one inserter in the gap that defines a well-defined return flow channel.
  • the return flow channel on the inserting device preferably has a small peripheral surface in comparison to its cross section. As a result, the wall friction is reduced at the return flow.
  • the large cross-sectional area compared to the peripheral surface allows high flow velocities of the damping medium without unduly increasing the flow resistance. Therefore, in addition, the insert means is constructed of such a material and so as to provide an average density of the insert means between the piping system and the damper chamber which is less than an average density of the damping medium. Such a measure ensures that weight can be saved.
  • the mean density of the cartridge is less than one-half of the mean density of the damping medium, or at least less than three quarters of the density of the damping medium.
  • At least one further throttle valve is provided as a lowering valve with a further field generating device.
  • the additional throttle valve as a lowering valve can be provided, for example, to lower the suspension fork when driving uphill or to keep lowered.
  • the further throttle valve as a lowering valve, as well as the above-described throttle valve may comprise an electric coil as a field-generating device. It is also possible that a remanence magnet and / or a permanent magnet is or are provided as a field-generating device. In all embodiments, the lowering valve is preferably connected in series with the throttle valve.
  • a corresponding magnetic field is generated with this field-generating device only if the lowering of the suspension fork when driving uphill is desired, for example, and when the suspension fork is in the rebound state. Then the increased damping ensures reliable positioning of the suspension fork in the lowered state. At the same time can still be a damping of shocks. After the climb, the lowering valve can be switched off again, so that the fork quickly returns to its normal rebound position during normal operation.
  • a permanent magnet is mechanically movable between a normal position and a further position such as a lowered position.
  • the permanent magnet For example, it may be provided on a rotatable device surrounding the outer tube. With an adjustment lever, the permanent magnet can be brought into the desired angular position, where it acts without contact through the standpipe on the lowering valve.
  • At least one one-way valve and / or at least one check valve is or are designed as a shim valve.
  • a shim valve may include a stack of different disks that provide non-linear response to the check valve.
  • At least one one-way valve and / or at least one check valve is adjustable. This can be done, for example, from the outside.
  • An adjustable valve device may consist of one valve or of two or more individual valves connected in series.
  • One of the valves can be designed as a check valve, which in particular purely mechanically z. B. as a shim valve, the damping medium in one direction only.
  • Another valve or partial valve may be integrated in the check valve of the adjustable valve device or be arranged adjacent to the check valve.
  • the further valve can operate on a mechanical and / or electrical and / or on a magnetorheological basis and dampen the flow through a damping channel of the further valve to the desired extent by generating or applying an adjustable, predetermined or fixed magnetic field.
  • the further valve within the adjustable valve device can be provided on the basis of remanence. Then the further valve is associated with an electrical coil for generating magnetic pulses, with which a permanently acting magnetic field in a hard or soft magnetic material is changed or adjusted.
  • the adjustable valve device at least a permanent magnet and / or at least one electrical coil for generating or application of a desired magnetic field.
  • At least one adjustable valve device comprises a remanence valve or consists of only one remanence valve which operates on a magnetorheological basis and whose magnetic field is adjustable by at least one pulse of an electrical coil.
  • At least one adjustable valve and / or at least one check valve is designed as an adjustable valve device.
  • Fig. 1 shows a suspension fork 1 according to the invention in a front view.
  • the suspension fork 1 has a control tube 2, to which a fork crown 51 is attached.
  • the two pipe systems 3 and 4 are arranged.
  • Each pipe system includes a standpipe and a dip tube.
  • the pipe system 3 comprises the standpipe 5 and the dip tube 7, while the pipe system 4 has the standpipe 6 and the dip tube 8.
  • the two dip tubes 7 and 8 are connected to each other via a connecting bracket 52.
  • Both pipe systems 3 and 4 are designed to be telescopic.
  • At the lower end of the suspension fork dropouts 53 and 54 are provided, between which an impeller of a bicycle can be arranged.
  • a damper device 10 is disposed in the pipe system 3, while in the pipe system 4, a spring device 50 is arranged.
  • Fig. 2 shows a schematic cross-sectional view of the pipe system 3 of the suspension fork Fig. 1 ,
  • the standpipe 3 is connected via the fork crown 51 with the frame of a bicycle, not shown.
  • the immersion tube 7 slides telescopically on the standpipe 5.
  • the damper device 10 is arranged, which comprises a damper chamber 12 which is divided by a piston 15 into a first chamber 16 and a second chamber 17.
  • the piston 15 is provided with a piston rod 14 extending through the first chamber 16 and out of the standpipe 5 addition extends.
  • the other end of the piston rod is connected to the lower end of the dip tube 7.
  • the throttle valve 13 is arranged, which is electrically adjustable here.
  • the throttle valve 13 is associated with a field generating device 30, which serves to generate a magnetic field.
  • a magnetorheological fluid is used here. Also conceivable is the use of electrorheological fluids.
  • a first one-way valve 21 is provided in the piston 15, which is otherwise designed as a pump piston.
  • the one-way valve 21 may be embodied as a shim valve, for example, and only allows the flow of the damping medium 11 from the second chamber 17 through the piston 15 into the first chamber 16 when the pressure within the second chamber 17 is greater than within the first chamber 16. In the opposite direction blocked the one-way valve 21st
  • the return flow channel 18 begins, through which the damping medium 11 can flow from the first chamber 16 to the throttle valve 13.
  • the damping medium 11 flowing in the direction of rotation 23 flows through the throttle valve 13, where it is damped in accordance with the settings of the field generating device 30.
  • the adjoining the throttle valve 13 connecting channel 19 leads to the second one-way valve 22, which opens in the direction of rotation 23 when the pressure in the connecting channel 19 is greater than the pressure in the second chamber 17.
  • the equalizing channel 28 branches the compensation chamber 24, in which a compensation volume 25 is present.
  • the compensating volume 25 may be, for example, a pressurized flexible bellows or a balloon or the like, which is separated from the volume of the compensation chamber 24 elastic. It is also possible to use a separating piston or a spring for prestressing.
  • the return flow channel 18 extends through the intermediate space between the damper chamber 12 and the inner circumferential surface of the standpipe 5. There is located in the space an insert means 38, which provides a defined cross-section for the return flow 18. Thereby, the volume of the damping medium 11 can be significantly reduced, since only the cross section of the return flow channel 18 is filled at the insert means 38 with the damping medium 11 and not the complete gap. Thereby, the weight of the damper device 10 and the entire suspension fork 1 can be significantly reduced.
  • a control device 32 is used for control.
  • the controller 32 is connected to sensors 33, which recognize the current state of the fork and respond accordingly.
  • sensors 33 which recognize the current state of the fork and respond accordingly.
  • a sensor device 33 can detect the spring travel 36 at short time intervals, so that from the time sequence of the signals it is also possible to conclude on relative speeds and thus on acceleration values.
  • the use of acceleration sensors is possible.
  • the spring travel 36 can be detected via a position detection of the sensor device 33 relative to a measuring device 65.
  • End position dampers 37 may be provided to prevent a stop of the dip tube 7 to the standpipe 5.
  • the volume corresponding to the plunging piston rod 14 must flow through the return flow channel 18 in the direction of circulation 23 to the throttle valve 13, where the damping channel 31 of the throttle valve 13 is exposed to the magnetic field of the field generating device 30.
  • the damping medium 11 flows a short distance through the connecting channel 19 and then through the compensation channel 28 into the compensation chamber 24.
  • the inflow of the damping medium 11 can be detected by the detector 64 of the sensor device 33 at the inlet into or within the compensation chamber 24. Since the detector plate used as a detector 64 bends or twisted here in the flow direction, can be deduced on the Druckmatnfall.
  • the damping medium 11 flowing through the return flow channel 18 flows through the throttle valve 13, where it is now exposed to a correspondingly adapted magnetic field of the field generating device 30.
  • the embodiment according to Fig. 2 can also use one electrically operated throttle valve 13 can be realized, in which a conventional oil is used as a damping medium.
  • Fig. 3 shows a further embodiment, wherein in a likewise highly schematic cross-section, the pipe system 3 of a fork 1 according to Fig. 1 is shown.
  • the pipe system 3 is according to Fig. 3 similarly constructed as the pipe system 3 according to Fig. 2 ,
  • the connecting channel 19 is divided after the throttle valve 13 but in two compensation channels 28 and 29 for exchange with the compensation chamber 24.
  • a first check valve 26 In the first compensation channel 28 from the throttle valve 13 to the compensation chamber 24 toward a first check valve 26 is provided which allows only a flow of the damping medium 11 from the throttle valve 13 into the compensation chamber 28 inside.
  • a sensor device 33 at the input of the compensation chamber can detect the direction 34 of the relative movement and thus close the pressure step case.
  • the second compensation channel 29 is provided, on which a second check valve 27 is arranged.
  • This check valve 29 opens only when the pressure in the compensation chamber 24 is greater than the pressure in the connecting channel 19th
  • the check valves 26 and 27 are adjustable. It is possible that controls are provided on the outside of the suspension fork, so that the check valves 26 and 27 are optionally operated while driving by the driver. These can z. B. may be provided according to dials on the fork crown. Also possible is an electric remote control.
  • the throttle valve 13 is an electrically adjustable throttle valve, and that a magnetorheological fluid is used as the damping medium 11.
  • the fork 1 according to Fig. 3 is operated with a magnetorheological fluid, it may still be the case to provide the check valves 25 and 26 adjustable or (pre-) adjustable, as this can be done to adapt to a basic curve. Depending on the situation, an adjustment of the throttle valve 13 can then take place.
  • Valves 62 and 63 are provided.
  • the valve 62 may be used for refilling or replacing damping medium 11, while the valve 63 is used, for example, to check the air pressure in the compensating volume 25 of the compensation chamber 24 or for refilling compressed air.
  • Fig. 4 shows another pipe system 4 for a fork 1 according to Fig. 1 ,
  • This pipe system 4 is basically similar in structure to the pipe system 4 according to the Fig. 2 and 3 ,
  • Fig. 2 indicates the pipe system according to Fig. 4 nor a lowering valve 42, which is arranged in series and here in front of the throttle valve 13.
  • the damper device 10 is equipped with my magnetorheological fluid as the damping medium 11, so that the field generating means 30 and 43 for the throttle valve 13 and the lowering valve 42 are provided.
  • the field generating device 43 may include an electrical coil 44 that generates a corresponding magnetic field. It is also possible that, for example, a remanence magnet 45 is provided whose field strength is required or periodic Distances by magnetic pulses of the electric coil 44 is set to the currently desired value. Thus, a permanent magnetic field can be generated in the remanence magnet 45, which is also available after switching off the current required for the electrical coil 44. If necessary, the magnetic field strength of the field generating device 43 can still be modified by a magnetic field of the electric coil 44.
  • a permanent magnet 46 may be provided on an outer operating lever, which is rotatably arranged, for example, around the standpipe 5. By positioning the permanent magnet 46 such that its magnetic field acts on the lowering valve 42 in the desired manner with a magnetic field, a corresponding magnetic field can be generated in the lowering valve 42. By turning away, the magnetic field no longer acts on the lowering valve 42.
  • Fig. 5 shows a typical cross section through a pipe system according to the Fig. 2 . 3 or 4 , In this case, the uncut damper chamber 12 can be seen in the middle. Radially outside the standpipe 5 of the pipe system 3 is shown in section. Radially outward, the opposite to the standpipe 5 telescoping dip tube 7 connects.
  • the deployment device 38 may be in one piece, but may also be formed of two or more parts.
  • the insert means 38 extends in the embodiments substantially over the length of the damper chamber 12, but may also be longer or shorter.
  • a return flow channel 18 is provided on the insert device 38.
  • the return flow channel 18 serves here as a return flow channel for the damping medium 11 on the way from the first chamber 11 via the throttle valve in the compensation chamber 24 or in the second chamber 17.
  • the return flow channel 18 may be about the shape shown here or other shapes such as round, square or rectangular shapes. In principle, any other shape is possible, such as an elliptical shape.
  • the ratio of the cross-sectional area as flow cross section 39 to the circumference of the return flow channel 18 is large, so that the flow resistance of the damping medium 11 in the return flow channel 18 remains relatively low even at high flow velocities.
  • the ratio of the largest diameter or the longest extent 40 to the width 48 is relatively small here.
  • the length 40 is smaller than the diameter 41 of the pipe system and in particular smaller than the radius of the pipe system, preferably also smaller than half the radius of the pipe system.
  • the flow cross section 39 is as large as necessary.
  • both channels z. B. have a rectangular or elliptical cross-section.
  • the other channel 55 can serve, for example, for carrying electrical lines or the like. It is also possible that both channels are used as return channels.
  • the insert means may be solid and it is also possible for the insert means 38 to have hollow regions or cavities, so that the average density of the inserter 38 is reduced.
  • the deployment device may be at least partially made of metal and / or plastic.
  • the average density of the inserter 38 at least in the region of the gap between the pipe system 4 and the damper chamber 12 is less than the density of the damping medium 11 and in particular at most half as large. As a result, a considerable proportion by weight can be saved. Experiments have shown that the weight of the damper device could be reduced by considerably more than 10%. Also 20% and more may be possible.
  • Fig. 6 shows a schematic cross section of an exemplary throttle valve shown 13.
  • a core 59 is centrally provided, which is surrounded by a wound electric coil as a field-generating device 30.
  • a total of four damping channels 31 are provided, of which two are separated from each other by a fan or a fan-like structure 57. This increases the effectiveness.
  • the field lines 61 with applied magnetic field pass through the core 59, approximately perpendicularly pass through a damping channel 31, the subsequent fan 57 and the second damping channel 31 and are through the ring 60 of a magnetically conductive material, here approximately in a semicircle around the Guided around core until at the bottom again two damping channels 31 are provided with intermediate fan wall 57 through which the field lines pass approximately vertically, so that total closed field lines 61 are present.
  • Fig. 4 only one field line is representative.
  • magnetic insulating materials 58 Adjacent to an electrical coil 30, magnetic insulating materials 58 are provided to shape the magnetic field as desired.
  • Fig. 7 shows a schematic cross section through a pipe system with a throttle valve.
  • the standpipe 5 is a cylinder with a wall 52 arranged.
  • the wall 52 defines the damper chamber 12.
  • a coil is provided as a magnetic device 30.
  • the coil is wound around the toroidal core 59.
  • the annular core 59 has a slot at one location. This slot forms the damping gap 55 through which the magnetorheological fluid must pass.
  • the damping gap 55 is acted upon by the magnetic field controlled by the electronic control device 32.
  • some magnetic field lines 61 are drawn in, which pass through the damping gap 55 approximately vertically. This embodiment enables a particularly energy-efficient damper.
  • the damper chamber 12 is provided.
  • the magnetic stress can be calculated by the product of the number of turns and the coil current.
  • the coil should now generate a defined magnetic field in the magnetic circuit, for. B. a certain magnetic flux or a field of certain magnetic field strength.
  • the coil may also be calculated as a single turn in which a correspondingly high current flows (namely, the coil current multiplied by the number of turns).
  • the losses result from the current squared and the electrical resistance.
  • the individual conductors can not be packed close to each other and due to the insulation and the geometric structure of the coil has a (copper) fill factor less than 100%.
  • Starting from the same number of turns and the same wire size means a higher fill factor a smaller coil.
  • the average winding length and thus also the electrical resistance decreases.
  • Fig. 7 shown construction a particularly low energy consumption achievable, which is very important and advantageous especially for outdoor products.
  • the invention provides an advantageous suspension fork, which has advantageous properties, in particular when using, for example, magnetorheological fluids. It is possible a large stroke, since the internals in the pipe system 3 can be made physically small. Normally, only a single throttle valve 13 is required in order to effectively and differently attenuate both in the pressure stage case as well as in Switzerlandcarenfall.
  • the total weight of the deployable fork can be reduced by almost 5% or more, which significantly increases its attractiveness for sporting and competitive use.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Electromagnetism (AREA)
  • Fluid-Damping Devices (AREA)
  • Axle Suspensions And Sidecars For Cycles (AREA)

Claims (13)

  1. Fourche de suspension (1) pour une bicyclette dotée d'un tube de direction (2) et d'au moins un système de tubes (3, 4) relié à celui-ci, lequel comprend un tube montant (5, 6) et un tube plongeur (7, 8) mobile par rapport audit tube montant (5, 6), un espace de logement de roue (9) étant prévu à côté du système de tubes (3, 4),
    un dispositif d'amortissement (10) doté d'un agent d'amortissement (11) étant prévu au sein du système de tubes (3, 4), ledit dispositif d'amortissement (10) disposant d'une chambre d'amortissement (12) et d'une vanne d'étranglement (13), la chambre d'amortissement (12) étant divisée en une première chambre (16) et en une deuxième chambre (17) par un piston (15) mobile et relié à une tige de piston (14), et la première chambre (16) étant reliée à la deuxième chambre (17) par le biais d'un canal de reflux (18), la vanne d'étranglement (13) et un canal de liaison (19), l'agent d'amortissement (11) comprenant un fluide magnéto-rhéologique (9) et la vanne d'étranglement (13) étant réglable, et au moins un dispositif de génération de champ (30) étant prévu pour générer un champ magnétique dans un canal d'amortissement (31) de la vanne d'étranglement (13), un circuit à sens unique (20) étant sensiblement prévu pour l'agent d'amortissement (11) dans lequel sont prévues au moins deux vannes anti-retour (21, 22) de telle sorte que, aussi bien lorsque la tige de piston (14) plonge dans la chambre d'amortissement (12) que lorsque la tige de piston (14) ressort de la chambre d'amortissement (12), l'agent d'amortissement (11) circule dans le même sens (23), une première des vannes anti-retour (21) étant agencée sur le piston (15), ladite première vanne autorisant un courant de l'agent d'amortissement (11) passant de la deuxième chambre (17) à la première chambre (16),
    et une deuxième vanne anti-retour (22) étant agencée sur le canal de liaison (19), ladite vanne anti-retour (22) autorisant un courant de l'agent d'amortissement (11) allant du canal de liaison (19) dans la deuxième chambre (17) de telle sorte qu'aussi bien le fait que la tige de piston (14) plonge dans la chambre d'amortissement (12) que celui que la tige de piston (14) ressorte de la chambre d'amortissement (12) peuvent être commandés de manière ciblée par la vanne d'étranglement (13) réglable,
    un dispositif de joint (38) entre le système de tubes (3) et la chambre d'amortissement (12) étant prévu, le canal de reflux (18) étant prévu au moyen partiellement sur le dispositif de joint (38) et limitant de préférence la section de passage (39) du canal de reflux (18),
    caractérisée en ce,
    qu'une densité moyenne du dispositif de joint (38) entre le système de tubes (3, 4) est inférieure à une densité moyenne de l'agent d'amortissement (11).
  2. Fourche de suspension selon la revendication 1, une chambre d'équilibrage (24) étant prévue avec un volume d'équilibrage (25) de précontrainte, ledit volume d'équilibrage (25) étant relié à la vanne d'étranglement (13) et à la deuxième chambre (17).
  3. Fourche de suspension selon la revendication précédente, la vanne d'étranglement (13) étant reliée à la chambre d'équilibrage (24) par un premier clapet de refoulement (26) qui n'autorise qu'un courant de l'agent d'amortissement (11) allant de la vanne d'étranglement (13) à la chambre d'équilibrage (24).
  4. Fourche de suspension selon l'une quelconque des deux revendications précédentes, la chambre d'équilibrage (24) étant reliée à la deuxième chambre (17) par un deuxième clapet de refoulement (27) qui n'autorise qu'un courant de l'agent d'amortissement (11) allant de la chambre d'équilibrage (24) à la deuxième chambre (17).
  5. Fourche de suspension selon l'une quelconque des deux revendications précédentes, au moins un clapet de refoulement (26, 27) étant réglable pour permettre une résistance de courant réglable dans l'action de compression et/ou dans l'action d'extension.
  6. Fourche de suspension selon l'une quelconque des revendications précédentes, un rapport entre le diamètre extérieur de la tige de piston et le diamètre extérieur du piston (14) étant de 0,2 à 0,4 et/ou un rapport entre le diamètre extérieur de la tige de piston et le diamètre extérieur du piston (14) étant adapté à un rapport prédéfini d'un amortissement de base dans l'action de compression et d'un amortissement de base dans l'action d'extension.
  7. Fourche de suspension selon la revendication précédente, comprenant au moins un dispositif de commande (32) et un dispositif capteur (33), ledit dispositif capteur (33) étant prévu pour détecter une mesure de vitesse relative et pour détecter notamment une mesure d'une vitesse relative du piston (15) par rapport à la chambre d'amortissement (12) et/ou le dispositif capteur (33) étant prévu pour détecter un sens (34, 35) du mouvement relatif du piston (15) par rapport à la chambre d'amortissement (12) et/ou le dispositif capteur (33) étant prévu pour détecter une mesure d'un débattement (36).
  8. Fourche de suspension selon l'une quelconque des revendications précédentes, au moins un amortissement de fin de course (37) étant prévu.
  9. Fourche de suspension selon l'une quelconque des revendications précédentes, la première chambre (16) étant, dans une application conforme, agencée en dessous de la deuxième chambre (17) et la vanne d'étranglement (13), elle, au-dessus de la chambre d'amortisseur (12)
  10. Fourche de suspension selon la revendication précédente, la chambre d'équilibrage (24) étant prévue au-dessus de la vanne d'étranglement (13).
  11. Fourche de suspension selon l'une quelconque des revendications précédentes, un diamètre maximal (40) d'une section de passage (39) du canal de reflux (18) au dispositif de joint (38) étant inférieur à un diamètre (41) et notamment inférieur à un rayon du système de tubes (3).
  12. Fourche de suspension selon l'une quelconque des revendications précédentes, une autre vanne d'étranglement étant prévue en tant que vanne de descente (42) dotée d'un autre dispositif de génération de champ (43), et la vanne de descente (42) étant notamment connectée en série avec la vanne d'étranglement (13).
  13. Fourche de suspension selon la revendication précédente, l'autre dispositif de génération de champ (43) comprenant une bobine électrique (44) et/ou un aimant rémanent (45) et/ou au moins un aimant permanent (46) déplaçable notamment entre une position normale et au moins une position de descente (47).
EP13004217.9A 2012-08-28 2013-08-27 Fourche suspendue, en particulier pour vélos Active EP2703686B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102012016946.9A DE102012016946A1 (de) 2012-08-28 2012-08-28 Federgabel, insbesondere für Fahrräder

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EP2703686A2 EP2703686A2 (fr) 2014-03-05
EP2703686A3 EP2703686A3 (fr) 2015-12-30
EP2703686B1 true EP2703686B1 (fr) 2018-02-14

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US (1) US8910963B2 (fr)
EP (1) EP2703686B1 (fr)
DE (1) DE102012016946A1 (fr)
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DE102015119505B4 (de) * 2015-07-21 2022-12-08 Inventus Engineering Gmbh Türkomponente mit einer steuerbaren Dämpfereinrichtung
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US8910963B2 (en) 2014-12-16
TWI515378B (zh) 2016-01-01
EP2703686A3 (fr) 2015-12-30
TW201422943A (zh) 2014-06-16
EP2703686A2 (fr) 2014-03-05
US20140062056A1 (en) 2014-03-06
DE102012016946A1 (de) 2014-03-06

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